JP6417535B2 - Compressor and refrigeration cycle apparatus using the same - Google Patents

Description

  The present invention relates to a compressor using a working fluid containing R1123 and a refrigeration cycle apparatus using the compressor.

  In general, the refrigeration cycle apparatus comprises a compressor, a four-way valve if necessary, a radiator (or a condenser), a decompressor such as a capillary tube or an expansion valve, an evaporator, etc., and constitutes a refrigeration cycle. Cooling or heating action is performed by circulating a refrigerant inside.

  As refrigerants in these refrigeration cycle apparatuses, chlorofluorocarbons (fluorocarbons are described as ROO or ROOXX are defined by the US ASHRAE 34 standard. Hereinafter, they are indicated as ROO or RXX. ) Or halogenated hydrocarbons derived from methane or ethane are known.

  R410A is often used as the refrigerant for the refrigeration cycle apparatus as described above, but the global warming potential (GWP) of the R410A refrigerant is as large as 1730, which is problematic from the viewpoint of preventing global warming.

  Thus, from the viewpoint of preventing global warming, for example, R1123 (1,1,2-trifluoroethylene) and R1132 (1,2-difluoroethylene) have been proposed as refrigerants having a small GWP (for example, patents). Document 1 or Patent document 2).

International Publication No. 2012/157774 International Publication No. 2012/157765

  However, R1123 (1,1,2-trifluoroethylene) and R1132 (1,2-difluoroethylene) are less stable than conventional refrigerants such as R410A and disproportionate when they generate radicals. There is a possibility of changing to another compound by the reaction. Since the disproportionation reaction involves a large heat release, the reliability of the compressor and the refrigeration cycle apparatus may be reduced. For this reason, when using R1123 and R1132 for a compressor and a refrigerating cycle device, it is necessary to suppress this disproportionation reaction.

  In consideration of the above-described conventional problems, the present invention specifies, for example, a compressor that is more suitable for using a working fluid including R1123 in a compressor used for an application such as an air conditioner. is there. In addition, the lubricating oil more suitable for using the working fluid containing R1123 is specified. In addition, the present invention provides a refrigeration cycle apparatus more suitable for using a working fluid containing R1123.

In order to solve the conventional problems, the present invention uses a refrigerant containing 1,1,2-trifluoroethylene as a working fluid, uses a polyol ester oil as a lubricating oil for a compressor, and at least one cylinder; A piston fitted in an eccentric part of a crankshaft provided in the cylinder; a vane that partitions the inside of the cylinder into a suction chamber and a compression chamber in accordance with the eccentric movement of the piston; One end plate, and a manganese phosphate coating is applied as a surface treatment of the crankshaft.

  The present invention can provide a compressor and a refrigeration cycle apparatus more suitable for using a working fluid containing R1123.

The longitudinal cross-sectional view of the rotary compressor in Embodiment 1 of this invention The expanded sectional view of the compression mechanism part of the rotary compressor in Embodiment 1 of this invention Assembly drawing of compression mechanism section in embodiment 1 of the present invention 1 is a schematic configuration diagram of a refrigeration cycle apparatus according to Embodiment 1 of the present invention. FIG. 2 is an enlarged cross-sectional view of a main part near the power supply terminal of the compressor according to the first embodiment of the present invention. Vertical section of a compressor according to Embodiment 2 of the present invention Schematic configuration diagram of a refrigeration cycle apparatus according to Embodiment 3 of the present invention. Mollier diagram for explaining the operation of the refrigeration cycle apparatus according to Embodiment 3 of the present invention. Mollier diagram for explaining the operation of the refrigeration cycle apparatus according to Embodiment 3 of the present invention. Mollier diagram for explaining the operation of the refrigeration cycle apparatus according to Embodiment 3 of the present invention. Schematic block diagram of the refrigerant pipe joint constituting the refrigeration cycle apparatus according to Embodiment 3 of the present invention. Schematic configuration diagram of a refrigeration cycle apparatus according to Embodiment 4 of the present invention. Schematic configuration diagram of a refrigeration cycle apparatus according to Embodiment 5 of the present invention. Mollier diagram for explaining the operation of the refrigeration cycle apparatus according to Embodiment 5 of the present invention.

  A first invention uses a refrigerant containing 1,1,2-trifluoroethylene as a working fluid, uses polyol ester oil as a lubricating oil for a compressor, and includes at least one cylinder and a crank provided in the cylinder. A piston fitted to an eccentric part of a shaft, a vane that partitions the inside of the cylinder into a suction chamber and a compression chamber in accordance with the eccentric movement of the piston, and two end plates that close both end faces of the cylinder, As a surface treatment for the crankshaft, a manganese phosphate coating is applied. According to this, it becomes possible to alleviate the sliding state of the sliding part with the upper bearing and the lower bearing supporting the crankshaft and the sliding part with the piston, and suppress the generation of local sliding heat. Therefore, the disproportionation reaction of R1123 can be suppressed. Moreover, since the carbonyl group of the polyol ester oil supplements a radical that triggers the disproportionation reaction, the disproportionation reaction of R1123 can be suppressed.

  According to a second aspect of the present invention, there is provided a fixed scroll and an orbiting scroll in which a spiral wrap rises from an end plate using a refrigerant containing 1,1,2-trifluoroethylene as a working fluid, using a polyol ester oil as a lubricating oil for a compressor. A compression chamber formed in both directions by meshing is provided, and a manganese phosphate coating is applied as a surface treatment of at least one of the fixed scroll and the orbiting scroll. According to this, since it becomes possible to relieve the sliding state of the sliding part of a fixed scroll and a turning scroll and generation | occurrence | production of local sliding heat can be suppressed, the disproportionation reaction of R1123 can be suppressed.

According to a third invention, in the first or second invention, the working fluid is a mixed working fluid containing difluoromethane, and the difluoromethane is 30 wt% or more and 60 wt% or less, or tetrafluoro A mixed working fluid containing ethane, wherein the tetrafluoroethane is 30 wt% to 60 wt%, or a mixed working fluid containing difluoromethane and tetrafluoroethane, the difluoromethane and tetrafluoroethane The mixing ratio of the difluoromethane and tetrafluoroethane is 30% by weight or more and 60% by weight or less. According to this, while suppressing the disproportionation reaction of R1123, a refrigerating capacity and COP can be improved.

  According to a fourth invention, in any one of the first to third inventions, the polyol ester oil constitutes at least one selected from the group consisting of neopentyl glycol, trimethylolpropane, pentaerythritol, dipentaerythritol. It is intended to be alcohol. According to this, since the viscosity of refrigerating machine oil can be adjusted freely, the oil film between a vane and a piston can be ensured and generation | occurrence | production of sliding heat can be suppressed.

  According to a fifth invention, in any one of the first to third inventions, the polyol ester oil contains a phosphate ester antiwear agent. According to this, the anti-decomposition reaction of the R1123 refrigerant is suppressed by suppressing the heat generation by adsorbing the antiwear agent on the surface of the sliding portion and reducing friction.

  According to a sixth invention, in any one of the first to third inventions, the polyol ester oil contains a phenolic antioxidant. According to this, since the phenol-based antioxidant quickly captures radicals generated at the sliding portion, the radicals are prevented from reacting with the refrigerant R1123.

  A seventh invention is the invention according to any one of the first to third inventions, wherein the polyol ester oil is mixed with a terpene or terpenoid of 1% or more and less than 50% with a lubricating oil having a viscosity higher than that of the base oil, or This is a lubricating oil in which an additive oil, which is mixed in advance with an ultra-high viscosity lubricating oil equivalent to or more than terpenes or terpenoids and adjusted to a viscosity equivalent to that of the base oil, is mixed with the base oil. According to this, the disproportionation reaction of R1123 can be suppressed.

  According to an eighth invention, in any one of the first to third inventions, the motor includes a motor unit that drives the piston or the orbiting scroll, and the motor includes a thermosetting insulating material on a conductor via an insulating film. An electric wire formed by coating and baking is used for a coil. According to this, by applying a thermosetting insulating material to the winding of the motor coil in the compressor, the resistance between the windings remains high even when the coil is immersed in liquid refrigerant, and the discharge is suppressed. As a result, the decomposition of the R1123 refrigerant can be suppressed.

  A ninth invention includes any one of the first to third inventions, further comprising a sealed container that houses the compression chamber and the motor unit, and the sealed container is installed in the mouth portion via an insulating member. A power supply terminal and a connection terminal for connecting the power supply terminal to a lead wire are provided, and a donut-shaped insulating member is disposed in close contact with the insulating member on the power supply terminal inside the sealed container. According to this, since the insulator is added to the power supply terminal inside the metal casing, it is possible to suppress insulation failure of the power supply terminal by extending the shortest distance between the conductors, and to prevent ignition due to the discharge energy of R1123. . Further, hydrogen fluoride generated when R1123 is decomposed is prevented from coming into contact with the glass insulator, and the glass insulator is prevented from being corroded and broken.

A tenth aspect of the invention is the compressor according to any one of the first to ninth aspects, a condenser that cools the refrigerant gas compressed by the compressor to a high pressure, and a high-pressure refrigerant liquefied by the condenser. Is a refrigeration cycle apparatus configured by connecting a throttle mechanism for decompressing the refrigerant and an evaporator for gasifying the refrigerant decompressed by the throttle mechanism through a pipe. According to this, while suppressing the disproportionation reaction of R1123, a refrigerating capacity and COP can be improved.

  An eleventh aspect of the invention is the tenth aspect of the invention, comprising condensation temperature detection means provided in the condenser, wherein a difference between the critical temperature of the working fluid and the condensation temperature detected by the condensation temperature detection means is 5K or more. Thus, the opening degree of the throttle mechanism is controlled. According to this, assuming that the working fluid temperature measured by the temperature detecting means corresponds to the pressure, the high pressure side working fluid temperature (pressure) is limited to 5K or more considering safety margin from the critical pressure. By controlling the opening of the throttle mechanism, it is possible to prevent excessively high condensing pressure from being excessively increased, so that disproportionation that may occur as a result of excessive pressure rise (as a result of close intermolecular distances) The reaction can be suppressed, and the reliability of the apparatus can be ensured.

  According to a twelfth aspect of the invention, in the tenth aspect of the invention, the high pressure side pressure detecting means provided between the discharge part of the compressor and the inlet of the throttle mechanism is provided, and the critical pressure of the working fluid and the high pressure side pressure are detected. The opening degree of the throttle mechanism is controlled so that the difference from the pressure detected by the means becomes 0.4 MPa or more. According to this, with respect to the working fluid including R1123, particularly when a non-azeotropic refrigerant having a large temperature gradient is used, the refrigerant pressure can be detected more accurately. Since the opening degree can be controlled and the high-pressure side pressure (condensation pressure) in the refrigeration cycle apparatus can be lowered, the disproportionation reaction can be suppressed and the reliability of the apparatus can be improved.

  A thirteenth invention is the tenth invention, further comprising condenser outlet temperature detection means provided between the condenser and the throttling mechanism, wherein the condensation temperature detected by the condensation temperature detection means and the condenser outlet The opening degree of the throttle mechanism is controlled so that the difference in the condenser outlet temperature detected by the temperature detecting means is 15K or less.

  According to this, by controlling the opening degree of the throttle mechanism using the detection result of the degree of supercooling indicated by the difference between the condensation temperature detection means and the condenser outlet temperature detection means, the working fluid in the refrigeration cycle apparatus is controlled. Since excessive pressure rise can be prevented, disproportionation reaction can be suppressed and the reliability of the apparatus can be improved.

  In a fourteenth aspect based on the tenth aspect, first conveying means for conveying a first medium that exchanges heat with the condenser, second conveying means for conveying a second medium that exchanges heat with the evaporator, Condensation temperature detection means provided in the condenser, first medium temperature detection means for detecting the temperature of the first medium before flowing into the condenser, and second medium before flowing into the evaporator Second medium temperature detecting means for detecting the temperature of the compressor, a change amount per unit time of the input of the compressor, a change amount per unit time of the input of the first transport means, and an input of the second transport means When the amount of change per unit time is smaller than a predetermined value, the amount of change per unit time of the condensation temperature detected by the condensation temperature detection means is detected by the first medium temperature detection means. Amount of change per unit time of temperature of one medium , Wherein when a is greater than any of the amount of change per unit time of the temperature of the second medium detecting a second medium temperature detecting means, and controls the throttle mechanism in the opening direction. According to this, when the appearance of the surrounding medium does not change, and when the condensing temperature changes suddenly, it is considered that the pressure increase due to the disproportionation reaction has occurred. To control. By doing so, it becomes possible to improve the reliability of the apparatus.

According to a fifteenth aspect, in any one of the tenth to fourteenth aspects, the outer periphery of a joint of a pipe constituting the refrigeration cycle is covered with a sealing agent containing a polymerization accelerator. According to this, when the working fluid leaks from the joint, the polymerization accelerator contained in the sealant and the working fluid containing R1123 undergo a polymerization reaction to generate a polymerization product. Leakage can be easily confirmed, and the polymerization product acts as a hindrance to the refrigerant flow released to the outside, and refrigerant leakage can be suppressed.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. Note that the present invention is not limited to the embodiments.

(Embodiment 1)
FIG. 4: has shown the system block diagram of the refrigerating-cycle apparatus using the compressor concerning the 1st Embodiment of this invention.

  As shown in FIG. 4, the refrigeration cycle apparatus according to the present embodiment is mainly composed of a compressor 61, a condenser 62, a throttle mechanism 63, and an evaporator 64, when described as a cooling-only cycle, for example. These devices are connected by piping so that a working fluid (refrigerant) circulates.

  In the refrigeration cycle apparatus configured as described above, the refrigerant changes to liquid by pressurization and cooling, and changes to gas by depressurization and heating. The compressor 61 is driven by a motor, pressurizes the low-temperature and low-pressure gas refrigerant into a high-temperature and high-pressure gas refrigerant, and is conveyed to the condenser 62. The condenser 62 is cooled and condensed by air blown by a fan or the like, and becomes a low-temperature and high-pressure liquid refrigerant. The liquid refrigerant is depressurized by the throttle mechanism 63, and part of the liquid refrigerant becomes low-temperature and low-pressure gas refrigerant, and the rest becomes low-temperature and low-pressure liquid refrigerant and is conveyed to the evaporator 64. The evaporator 64 is heated and evaporated by air blown by a fan or the like, and becomes a low-temperature and low-pressure gaseous refrigerant, which is again sucked into the compressor 61 and pressurized.

  In the above embodiment, the refrigeration cycle apparatus dedicated to cooling has been described. However, it is of course possible to operate the apparatus as a heating cycle apparatus via a four-way valve or the like.

  The heat transfer tube constituting the refrigerant flow path of at least one of the condenser 62 and the evaporator 64 is preferably an aluminum refrigerant tube containing aluminum or an aluminum alloy. A flat tube having a flow hole is desirable for reducing the condensation temperature or raising the evaporation temperature.

  The working fluid (refrigerant) sealed in the refrigeration cycle apparatus according to the present embodiment is a two-component mixture composed of (1) R1123 (1,1,2-trifluoroethylene) and (2) R32 (difluoromethane). In particular, it is a mixed working fluid having R32 of 30 wt% or more and 60 wt% or less.

  In application to a compressor described later, the disproportionation reaction of R1123 can be suppressed by mixing R32 with 30 wt% or more of R1123. Further, the higher the concentration of R32, the more the disproportionation reaction can be suppressed. This is because the action of mitigating the disproportionation reaction due to the small polarization of R32 to the fluorine atom and the behavior at the time of phase change such as condensation and evaporation are integrated because R1123 and R32 have similar physical characteristics. The disproportionation reaction of R1123 can be suppressed by the action of reducing the disproportionation reaction opportunity due to.

  Further, the mixed refrigerant of R1123 and R32 has an azeotropic boiling point with R32 being 30% by weight and R1123 being 70%, and there is no temperature slip, so that it can be handled in the same manner as a single refrigerant. That is, if R32 is mixed by 60% by weight or more, temperature slip increases, and handling similar to that of a single refrigerant may be difficult. Therefore, it is desirable to mix R32 at 60% by weight or less. In particular, it is desirable to mix R32 in an amount of 40 wt% to 50 wt% in order to prevent disproportionation and to make the temperature slip smaller because it approaches the azeotropic point and to facilitate device design.

  Tables 1 and 2 show that in the mixed working fluid of R1123 and R32, the pressure, temperature, and compressor displacement of the refrigeration cycle are the same when R32 is 30 wt% to 60 wt%. Refrigeration capacity and cycle efficiency (COP) are calculated and compared with R410A and R1123.

  First, calculation conditions in Tables 1 and 2 will be described. In recent years, in order to improve the cycle efficiency of equipment, the performance of heat exchangers has increased, and in actual operating conditions, the condensation temperature tends to decrease, the evaporation temperature tends to increase, and the discharge temperature also tends to decrease . Therefore, considering the actual operating conditions, the cooling calculation conditions in Table 1 correspond to the cooling operation of the air conditioner (indoor dry bulb temperature 27 ° C, wet bulb temperature 19 ° C, outdoor dry bulb temperature 35 ° C). The evaporation temperature was 15 ° C., the condensation temperature was 45 ° C., the superheated degree of the refrigerant sucked into the compressor was 5 ° C., and the supercooling degree at the condenser outlet was 8 ° C. The heating calculation conditions in Table 2 are the calculation conditions corresponding to the heating operation of the air conditioner (indoor dry bulb temperature 20 ° C, outdoor dry bulb temperature 7 ° C, wet bulb temperature 6 ° C), and the evaporation temperature is 2 ° C. The condensation temperature was 38 ° C., the superheat degree of the refrigerant sucked into the compressor was 2 ° C., and the supercool degree at the condenser outlet was 12 ° C.

From Table 1 and Table 2, mixing R32 at 30 wt% or more and 60 wt% or less increases the refrigeration capacity by about 20% compared to R410A during cooling and heating operation, and the cycle efficiency (COP) is It becomes 94 to 97%, and the global warming potential can be reduced to 10 to 20% of R410A.

  As described above, in the two-component system of R1123 and R32, taking into consideration the prevention of disproportionation, the magnitude of temperature slip, the capacity during cooling operation / heating operation, and COP (that is, compression described later) When a mixing ratio suitable for an air-conditioning apparatus using an air conditioner is specified, a mixture containing 30% by weight or more and 60% by weight or less R32 is desirable, and a mixture containing 40% by weight or more and 50% by weight or less R32 is more desirable. Is desirable.

<Modification 1 of working fluid>
The working fluid sealed in the refrigeration cycle apparatus of the present embodiment is (1) R1123 (1, 1
, 2-trifluoroethylene) and (2) R125 (tetrafluoroethane), a two-component mixed working fluid. In particular, R125 may be a mixed working fluid of 30 wt% to 60 wt%. .

  In application to a compressor described later, the disproportionation reaction of R1123 can be suppressed by mixing R125 in an amount of 30% by weight or more. Further, the higher the concentration of R125, the more the disproportionation reaction can be suppressed. This is because the disproportionation reaction due to the small polarization of R125 to fluorine atoms and the behavior during phase change such as condensation and evaporation are integrated because R1123 and R125 have similar physical characteristics. The disproportionation reaction of R1123 can be suppressed by the action of reducing the disproportionation reaction opportunity due to. Moreover, since R125 is a nonflammable refrigerant, R125 can reduce the combustibility of R1123.

  Tables 3 and 4 show that, in the mixed working fluid of R1123 and R125, the pressure, temperature of the refrigeration cycle, and the displacement of the compressor are the same at a mixing ratio where R125 is 30 wt% or more and 60 wt% or less. Refrigeration capacity and cycle efficiency (COP) are calculated and compared with R410A and R1123. The calculation conditions are the same as those in Tables 1 and 2.

From Tables 3 and 4, by mixing R125 at 30 wt% or more and 60 wt% or less, the refrigerating capacity is 96 to 110% and the cycle efficiency (COP) is 94 to 97% compared to R410A. .

  In particular, by mixing R125 at 40 wt% or more and 50 wt% or less, it is possible to prevent disproportionation of R1123 and to reduce the discharge temperature. Becomes easy. Furthermore, the warming potential can be reduced to 50-100% of R410A.

As described above, in the two-component system of R1123 and R125, when considering disproportionation, reduction in combustibility, ability during cooling operation / heating operation, COP, and discharge temperature (that is, described later) When a mixing ratio suitable for an air-conditioning apparatus using a compressor is specified, a mixture containing 30 wt% or more and 60 wt% or less of R125 is desirable, and more desirably 40 wt% or more and 50 wt% or less of R125. Mixtures containing are desirable.

<Modification 2 of working fluid>
The working fluid sealed in the refrigeration cycle apparatus of the present embodiment includes (1) R1123 (1,1,2-trifluoroethylene), (2) R32 (difluoromethane), and (3) R125 (tetrafluoroethane). In particular, a mixed working fluid in which the mixing ratio of R32 and R125 is 30 or more and less than 60% by weight and the mixing ratio of R1123 is 40% or more and less than 70% by weight. It may be.

  In application to a compressor, which will be described later, the mixing ratio of R32 and R125 is 30% by weight or more, and the disproportionation reaction of R1123 can be suppressed. Further, the higher the mixing ratio of R32 and R125, the more the disproportionation reaction can be suppressed. R125 also reduces the combustibility of R1123.

  Tables 5 and 6 show that refrigeration capacity and cycle efficiency when the mixing ratio of R32 and R125 is fixed to 50% by weight and the pressure, temperature, and displacement of the compressor when the mixture is mixed with R1123 are the same ( COP) is calculated and compared with R410A and R1123. The calculation conditions are the same as those in Tables 1 and 2.

From Tables 5 and 6, the mixing ratio of R32 and R125 is 30% by weight or more and 60% by weight or less. Compared with R410A, the refrigerating capacity is 107 to 116%, and the cycle efficiency (COP) is 93 to 96. %.

In particular, when the mixing ratio of R32 and R125 is 40% by weight or more and 50% by weight or less, disproportionation can be prevented, discharge temperature can be reduced, and combustibility can also be reduced. Furthermore, the warming potential can be reduced to 60-30% of R410A.

  In <Working fluid modification 2>, the mixing ratio of R32 and R125 of the three-component working fluid is described as 50% by weight, but the mixing ratio of R32 is set to 0% by weight to 100% by weight. If it is desired to increase the refrigerating capacity, increasing the mixing ratio of R32, conversely decreasing the mixing ratio of R32, and increasing the mixing ratio of R125 will reduce the discharge temperature and reduce the combustibility. be able to.

  As described above, in the three-component system of R1123, R32, and R125, when taking into consideration comprehensively the prevention of disproportionation, reduction of combustibility, ability during cooling operation / heating operation, COP, and discharge temperature (that is, When a mixing ratio suitable for an air conditioner using a compressor described later is specified), a mixture in which R32 and R125 are mixed and the sum of R32 and R125 is 30 wt% or more and 60 wt% or less is desirable. Desirably, a mixture containing 40 wt% or more and 50 wt% or less of the sum of R32 and R125 is desirable.

  FIG. 1 is a longitudinal sectional view of a hermetic compressor according to a first embodiment. FIG. 2 is an enlarged view of the compression mechanism section in the first embodiment. 1 and 2, the rotary compressor is one in which an electric motor (motor unit) 2 and a compression mechanism unit 3 are connected by a crankshaft 31 and housed in a sealed container 1, and the compression mechanism unit 3 includes a cylinder 30. The suction chamber 49 and the compression chamber 39 formed by the end plate 34 of the upper bearing 34 a and the end plate 35 of the lower bearing 35 a that close both ends of the cylinder 30, and the upper bearing 34 a and the lower bearing 35 a in the cylinder 30. The piston 32 fitted to the eccentric part 31a of the crankshaft 31 supported by the cylinder 32, and the vane which reciprocates following the eccentric rotation on the outer periphery of the piston 32 to partition the inside of the cylinder 30 into a suction chamber 49 and a compression chamber 39 33 is provided.

  The crankshaft 31 is provided with an oil hole 41 in the axial line portion, and oil supply holes 42 and 43 communicating with the oil hole 41 are provided on the wall portions of the upper bearing 34a and the lower bearing 35a, respectively. An oil supply hole 44 communicating with the oil hole 41 is provided in the wall portion of the crankshaft 31 with respect to the eccentric portion 31a, and an oil groove 45 is formed in the outer peripheral portion.

  On the other hand, a suction port 40 for sucking gas toward the suction portion is opened in the cylinder 30, and a discharge port 38 for discharging gas from a compression chamber 39 formed by turning from the suction chamber 49 is formed in the upper bearing 34a. Opened. The discharge port 38 is formed as a circular hole in plan view that passes through the upper bearing 34a, and a discharge valve 36 that is released when a pressure of a predetermined magnitude or more is provided on the upper surface of the discharge port 38. And a cup muffler 37 that covers the discharge valve 36.

  In the compression mechanism 3, the sliding contact portion of the piston 32 passes through the suction port 40 and moves away from the suction chamber 49 while gradually expanding, and sucks gas from the suction port 40 into the suction chamber. On the other hand, on the compression chamber side, the sliding portion of the piston 32 approaches the discharge port 38 while gradually reducing the compression chamber 39, and when the pressure is compressed to a predetermined pressure or higher, the discharge valve 36 opens and the gas is discharged from the discharge port 38. Is discharged from the cup muffler 37 into the sealed container 1. The gas discharged into the sealed container 1 is discharged from the discharge pipe 23 to the refrigeration cycle.

  The discharge port 38 is formed as a circular hole in plan view that passes through the upper bearing 34a, and a discharge valve 36 that is released when a pressure of a predetermined magnitude or more is provided on the upper surface of the discharge port 38. And a cup muffler 37 that covers the discharge valve 36.

On the other hand, the space 46 surrounded by the eccentric part 31a of the crankshaft 31, the end plate 34 of the upper bearing 34a and the inner peripheral surface of the piston 32, the inner part of the eccentric part 31a of the crankshaft 31, the end plate 35 of the lower bearing 35a and the piston 32. A space 47 surrounded by the peripheral surface is formed. Oil leaks into the spaces 46 and 47 from the oil hole 41 through the oil supply holes 42 and 43. The pressure in the spaces 46 and 47 is almost always higher than the pressure in the compression chamber 39, and is almost in the same state as the discharge pressure.

  The height of the cylinder 30 must be set slightly larger than the height of the piston 32 so that the piston 32 can slide inside. As a result, the end face of the piston 32, the upper bearing 34a, the lower bearing There is a gap between the end face of 35a. Therefore, oil leaks from the spaces 46 and 47 to the compression chamber 39 through this gap.

  Manganese phosphate film treatment is performed on the surface of the crankshaft 31.

  In the rotary compressor configured as described above, the surface of the crankshaft 31 is subjected to manganese phosphate coating treatment, whereby the sliding portion of the upper bearing 34a and the lower bearing 35a that support the crankshaft 31 and the piston 32 are provided. It is possible to alleviate the sliding state of the sliding portion, and the generation of local sliding heat can be suppressed, so that the disproportionation reaction of R1123 can be suppressed.

  In the compressor of the present embodiment, polyol ester oil is used as a lubricating oil for a compressor (refrigerating machine oil). The polyol ester of the present invention is not particularly limited, but by using at least one selected from the group consisting of neopentyl glycol, trimethylolpropane, pentaerythritol, dipentaerythritol as a constituent alcohol, the viscosity of the refrigerating machine oil Can be adjusted widely. According to this, since the viscosity of refrigerating machine oil can be adjusted freely, the oil film between a vane and a piston can be ensured and generation | occurrence | production of sliding heat can be suppressed. Since the carbonyl group of the polyol ester oil captures radicals that trigger the disproportionation reaction, the disproportionation reaction of R1123 can be suppressed.

  Moreover, although it does not specifically limit as a constituent fatty acid of the polyol ester of this invention, It is optimal to use a C6-C12 fatty acid. The constituent fatty acid may be a straight-chain fatty acid or a branched-chain fatty acid, but the straight-chain fatty acid has a higher ability to trap radicals because the carbonyl group is not sterically shielded by an alkyl group.

  Moreover, as an additive added to the lubricating oil for compressors, an antiwear agent, an antioxidant, a polymerization inhibitor, and a reactant adsorbent can be used. Antiwear agents include phosphate ester, phosphite, thiophosphate, and the like, but phosphate ester is most suitable because it does not adversely affect the refrigeration cycle.

  Specific examples of phosphate esters include tributyl phosphate, tripentyl phosphate, trihexyl phosphate, triheptyl phosphate, trioctyl phosphate, trinonyl phosphate, tridecyl phosphate, triundecyl phosphate, tridodecyl phosphate, tritridecyl phosphate, tritridecyl phosphate Tetradecyl phosphate, tripentadecyl phosphate, trihexadecyl phosphate, triheptadecyl phosphate, trioctadecyl phosphate, trioleyl phosphate, triphenyl phosphate, tricresyl phosphate, trixylenyl phosphate, cresyl diphenyl phosphate, xylenyl diphenyl A phosphate etc. are mentioned. Normally, phosphate ester antiwear agent is added to the refrigerating machine oil in an amount of 0.1 to 3 wt%, so that it can be effectively adsorbed on the surface of the sliding part to create a film with a small shearing force on the sliding surface. Abrasion prevention effect is obtained.

  According to this, the anti-decomposition reaction of the R1123 refrigerant is suppressed by suppressing the heat generation by the antiwear agent adsorbing on the surface of the sliding portion and reducing the friction.

  Specific examples of phenolic antioxidants include propyl gallate, 2,4,5-trihydroxybutyrophenone, t-butylhydroquinone, nordihydroguaiaretic acid, butylhydroxyanisole, 4-hydroxymethyl-2,6. -Di-t-butylphenol, octyl gallate, butylhydroxytoluene, dodecyl gallate and the like can be used. By adding 0.1 to 1 wt% of these antioxidants with respect to the base oil, radicals can be efficiently captured and reaction can be prevented. Further, coloring of the base oil itself by the antioxidant can be minimized.

  According to this, the phenol-based antioxidant efficiently captures radicals generated in the sealed container 1, thereby obtaining an effect of suppressing the decomposition reaction of R1123.

  In order to prevent a reaction of a highly reactive molecule containing a double bond and a fluorine atom such as R1123, about 5% of limonene may be added to the refrigerant amount of R1123. The compressor of the present invention and the refrigeration cycle apparatus using the compressor are closed systems, and as described above, lubricating oil is enclosed as a base oil. Generally, the viscosity of the lubricating oil which is the base oil enclosed in such a compressor is generally about 32 mm2 / s to 68 mm2 / s, while the viscosity of limonene is about 0.8 mm2 / s, which is a considerably low viscosity. When about 5% is mixed, the viscosity is drastically reduced to 60 mm2 / s, when 15% is mixed, 48 mm2 / s, and when 35% is mixed, 32 mm2 / s. Therefore, mixing a large amount of limonene to prevent the reaction of R1123 will affect the reliability of compressors and refrigeration cycle equipment, such as wear due to poor lubrication due to lowering of the viscosity of the lubricating oil and generation of metal soap due to metal contact with the sliding surface. To do.

  The lubricating oil of the compressor according to the present embodiment is preliminarily based on a high-viscosity lubricating oil or a mixture of limonene in order to compensate for a decrease in the viscosity of the base oil caused by the mixing of an amount of limonene suitable for preventing reaction. An appropriate lubricating oil viscosity is ensured by mixing an ultra-high viscosity lubricating oil in an amount equal to or greater than the amount.

  Specifically, the viscosity of the lubricating oil when mixing 5% limonene is 78 mm2 / s, and the viscosity of the lubricating oil when mixing 35% limonene is about 230 mm2 / s, so that 68 mm2 / s can be secured. . In order to maximize the effect of preventing the reaction of R1123 by limonene, extreme examples such as increasing the mixing amount of limonene to 70% or 80% are conceivable, but the viscosity of the base high-viscosity lubricating oil is 8500 mm 2/2 respectively. s or 25000 mm2 / s, which exceeds the maximum value of ISO standard of 3200 mm2 / s, and it is difficult to achieve uniform application with limonene, making practical application difficult.

  In addition, when mixing an equal amount of ultrahigh viscosity lubricating oil with limonene, a viscosity of 32 mm2 / s to 68 mm2 / s can be obtained by mixing a lubricating oil of 800 mm2 / s to 1000 mm2 / s. When mixing limonene and an ultra-high viscosity oil having different viscosity differences, a lubricating oil having a relatively uniform composition viscosity can be obtained by mixing the limonene while adding the ultra-high viscosity oil little by little.

  In this embodiment, limonene is used as an example. However, similar effects can be obtained if terpenes or terpenoids are used. Compressor and refrigeration cycle equipment such as pinene and sesquiterpenes farnesyl diphosphate, artemisinin, bisabolol, diterpenes geranylgeranyl diphosphate, retinol, retinal, phytol, paclitaxel, forskolin, aphidicolin and triterpenes squalene, lanosterol It can be selected according to the operating temperature and the required lubricating oil viscosity.

Further, the viscosity described is a specific example in a compressor having a high-pressure vessel, and further 5 m
Needless to say, the same effect can be obtained with a compressor of a low-pressure vessel used at a low lubricating oil viscosity of m2 / s to 32 mm2 / s.

  Note that terpenes such as limonene and terpenoids have solubility in plastics, but if they are mixed at about 30% or less, the effect is slight, and the electrical insulation required for the plastics in the compressor is a problem. It is not a level. However, it is desirable to use polyimide, polyimide amide, or polyphenylene sulfide having chemical resistance when there is a problem such as when long-term reliability is required or when the use temperature is constantly high.

  Moreover, as for the winding of the motor 2 of the compressor of this Embodiment, the varnish (thermosetting insulating material) is apply | coated and baked through the insulating film on the conductor. Examples of the thermosetting insulating material include a polyimide resin, an epoxy resin, and an unsaturated polyester resin. Among these, the polyimide resin can be converted into a polyimide by coating in the state of polyamic acid as a precursor and baking at around 300 ° C. It is known that the imidization reaction occurs by a reaction between an amine and a carboxylic anhydride. Since the R1123 refrigerant may react even in a short circuit between electrodes, a polyimide acid varnish mainly composed of a polyimide precursor formed by reacting an aromatic diamine and an aromatic tetracarboxylic dianhydride on a motor winding is used. By applying, a short circuit between electrodes can be prevented.

  For this reason, even when the coil of the motor 2 is immersed in the liquid refrigerant, it becomes possible to keep the resistance between the windings high, thereby suppressing the discharge between the windings and consequently suppressing the self-decomposition reaction of the R1123 refrigerant. An effect is obtained.

  FIG. 5 is a partial cross-sectional view showing the structure near the power supply terminal of the compressor according to the present embodiment. In FIG. 5, 71 is a power supply terminal, 72 is a glass insulator, 73 is a metal lid for holding a power supply terminal, 74 is a flag terminal connected to the power supply terminal, and 75 is a lead wire. In the compressor according to the present embodiment, a donut-shaped insulating member 76 that is in close contact with the insulating member is disposed on the power supply terminal inside the hermetic container 1 of the compressor. The most suitable donut-shaped insulating member is an insulating member that is resistant to hydrofluoric acid. Examples thereof include ceramic insulators and HNBR rubber donut spacers. Although it is essential that the doughnut-shaped insulating member is in close contact with the glass insulator, it is preferable that the donut-like insulating member is in close contact with the connection terminal.

  The power supply terminal configured in this manner has a long creepage distance between the power supply terminal and the inner surface of the compressor due to the donut-shaped insulating member, thereby preventing terminal tracking and preventing ignition due to the discharge energy of R1123. Can do. Further, hydrofluoric acid generated by the decomposition of R1123 is prevented from corroding the glass insulator.

  The compressor according to the present embodiment may be a so-called high-pressure shell type compressor in which the discharge port is opened in the sealed container 1 and the inside of the sealed container 1 is filled with the refrigerant compressed in the compression chamber 15. In the case of a so-called low-pressure shell type compressor in which the suction port 18 is opened in the sealed container 1 and the sealed container 1 is filled with the refrigerant before being compressed in the compression chamber 15, it is heated in the sealed container 1. In the configuration in which the temperature is likely to rise before being introduced into the compression chamber 15, the temperature reduction due to the introduction of the low-temperature refrigerant in the compression chamber 15 becomes more remarkable, which is desirable for suppressing the disproportionation reaction of R1123.

Further, even in a high-pressure shell type compressor, after the refrigerant discharged from the discharge port passes around the motor unit 2 and is heated by the motor unit 2 in the sealed container 1, the refrigerant is discharged from the discharge pipe 23 to the outside of the sealed container 1. You may comprise so that it may discharge to. According to this, even if the temperature of the refrigerant discharged from the discharge pipe 23 is equal, the refrigerant temperature in the compression chamber 15 can be lowered, which is desirable in suppressing the disproportionation reaction of R1123.
(Embodiment 2)
The second embodiment is different from the first embodiment in that the type of the compressor is different. FIG. 6 is a longitudinal sectional view of a scroll compressor according to the second embodiment of the present invention. Hereinafter, operation | movement and an effect | action are demonstrated about a scroll compressor.

  As shown in FIG. 6, the scroll compressor according to the second embodiment of the present invention is configured to include a hermetic container 7, a motor part (electric motor) 8, and a compression mechanism part (compression mechanism) 9 inside thereof. . The compression mechanism 9 includes a crankshaft 10 driven by an electric motor 8, a turning scroll 11, a fixed scroll 12, and an Oldham ring 13 that supports the turning scroll 11 to make a turning motion without rotating with respect to the fixed scroll 12. And the frame 14 for supporting the Oldham ring 13 so as to be movable for the support.

  The crankshaft 10 is supported by bearings 16 and 17 of the frame 14. A shaft 11 a of the orbiting scroll 11 is supported by a bearing 10 c provided on the crank portion 10 a of the crankshaft 10, and is engaged with the fixed scroll 12 to form a compression chamber 15. In addition, 18 is an inlet and 19 is an outlet.

  Manganese phosphate film treatment is performed on the sliding surfaces of the fixed scroll 12 and the orbiting scroll 11.

  Reference numeral 16 of the sealed container 7 is a suction pipe connected to the evaporator 64, and 23 is a discharge pipe connected to the condenser 62.

  An oil sump 20 is provided in the lowermost part of the hermetic container 7, and compressor lubricating oil (lubricating oil, refrigerating machine oil) 21 in the oil sump 20 is supplied to the lubrication target portion through the oil supply passage 10 b of the crankshaft 10. However, the bearing 16 is supplied from the oil supply hole 10d.

  About the scroll compressor comprised as mentioned above, the operation | movement and an effect | action are demonstrated below.

  When the crankshaft 10 is rotated by being driven by the electric motor 8, the orbiting scroll 11 is swung through the Oldham ring 13 and sucks the gas refrigerant from the suction pipe 22 to the suction port 18. In the compression chamber 15, the gas refrigerant is compressed while being reduced in volume while being moved from the outer peripheral side leading to the suction port 18 to the inner peripheral side leading to the discharge port 19, and discharged from the discharge port 19 into the sealed container 7. The high-temperature and high-pressure gas refrigerant is supplied to the refrigeration cycle from the discharge pipe 23, but is liquefied by the condenser 62, depressurized by the throttle mechanism 63, becomes two-phase, and reaches the evaporator 64. Thereafter, the two-phase refrigerant is gasified by the evaporator 64 and reaches the suction pipe 22 of the scroll compressor.

  In the scroll compressor configured as described above, the sliding surface of the fixed scroll 12 and the orbiting scroll 11 is subjected to the manganese phosphate coating on the sliding surfaces of the fixed scroll 12 and the orbiting scroll 11 to slide the sliding portion of the fixed scroll 12 and the orbiting scroll 11. Since the state can be relaxed and the generation of local sliding heat can be suppressed, the disproportionation reaction of R1123 can be suppressed. The same effect can be expected when the manganese phosphate film treatment is performed on only one of the orbiting scroll 11 and the fixed scroll 12.

(Embodiment 3)
FIG. 7 shows a refrigeration cycle apparatus 101 according to the third embodiment of the present invention. In the refrigeration cycle apparatus 101 according to the present embodiment, a compressor 102, a condenser 103, an expansion valve 104 that is a throttle mechanism, and an evaporator 105 are connected in this order through a refrigerant pipe 106 to constitute a refrigeration cycle circuit. A working fluid (refrigerant) is enclosed in the refrigeration cycle circuit.

  Next, the configuration of the refrigeration cycle apparatus will be described.

  For the condenser 103 and the evaporator 105, when the surrounding medium is air, a fin and tube heat exchanger, a parallel flow type (microtube type) heat exchanger, or the like is used.

  On the other hand, when the surrounding medium is brine or a refrigerant of a binary refrigeration cycle, the condenser 103 and the evaporator 105 are a double tube heat exchanger, a plate heat exchanger, or a shell and tube heat exchanger. It is done.

  As the expansion valve 104, for example, a pulse motor drive type electronic expansion valve is used.

  The refrigeration cycle apparatus 101 includes a fluid machine (first conveying means) 107 a that drives (flows) an ambient medium (first medium) that exchanges heat with refrigerant in the condenser 103 to a heat exchange surface of the condenser 103. Is installed. Further, the refrigeration cycle apparatus 101 includes a fluid machine (second transport means) that drives (flows) an ambient medium (second medium) that exchanges heat with the refrigerant in the evaporator 105 to a heat exchange surface of the evaporator 105. 107b is installed.

  As the surrounding medium, air in the atmosphere may be used, or water or brine such as ethyl glycol may be used. In the case where the refrigeration cycle apparatus 101 is a two-way refrigeration cycle, refrigeration is performed. Preferred refrigerants for the cycle and operating temperature range, such as hydrofluorocarbon (HFC), hydrocarbon (HC), carbon dioxide, etc. are used.

  In the fluid machines 107a and 107b for driving the surrounding medium, when the surrounding medium is air, an axial flow fan such as a propeller fan, a cross flow fan, a centrifugal blower such as a turbo blower is used, and when the surrounding medium is brine, A centrifugal pump or the like is used.

  When the refrigeration cycle apparatus 101 is a two-way refrigeration cycle, the compressor is responsible for the fluid machines 107a and 107b for transporting the surrounding medium.

  In the condenser 103, a condensing temperature detecting means is provided at a location where the refrigerant flowing in the condenser 103 flows in two phases (a state where gas and liquid are mixed) (hereinafter referred to as “two-phase tube of the condenser”). 110a is installed, and the refrigerant temperature can be measured.

  A condenser outlet temperature detecting means 110b is installed between the outlet of the condenser 103 and the inlet of the expansion valve 104. The condenser outlet temperature detection means 110b can detect the degree of supercooling at the inlet of the expansion valve 104 (a value obtained by subtracting the condenser temperature from the expansion valve inlet temperature).

  In the evaporator 105, an evaporation temperature detecting means 110 c is provided at a location where the refrigerant flowing in the two-phase flows (hereinafter referred to as “two-phase pipe of the evaporator” in this specification). The temperature of the refrigerant can be measured.

  A suction temperature detecting means 110d is provided in the compressor 102 suction section (between the evaporator 105 outlet and the compressor 102 inlet). Thereby, the temperature (intake temperature) of the refrigerant sucked into the compressor 102 can be measured.

  For the temperature detection means 110a to 110d, for example, an electronic thermostat that is contact-connected with a pipe through which a refrigerant flows or an outer pipe of a heat transfer pipe may be used, or a sheath pipe type that directly contacts the working fluid. In some cases, an electronic thermostat is used.

  Between the outlet of the condenser 103 and the inlet of the expansion valve 104, a high pressure side pressure detecting means for detecting the pressure on the high pressure side of the refrigeration cycle (the region where the refrigerant from the outlet of the compressor 102 to the inlet of the expansion valve 104 exists at a high pressure). 115a is installed.

  At the outlet of the expansion valve 104, low-pressure side pressure detection means 115b for detecting the pressure on the low pressure side of the refrigeration cycle (the region where the refrigerant from the outlet of the expansion valve 104 to the inlet of the compressor 102 exists at a low pressure) is installed.

  As the pressure detection means 115a and 115b, for example, a device that converts the displacement of the diaphragm into an electrical signal is used. A differential pressure gauge (measuring means for measuring the pressure difference at the inlet / outlet of the expansion valve 104) may be used instead of the high pressure side pressure detecting means 115a and the low pressure side pressure detecting means 115b.

  In the above description of the configuration, the temperature detection units 110a to 110d and the pressure detection units 115a and 115b are described as being all provided. However, in the control described later, the detection unit that does not use the detection value can be omitted. Needless to say.

  A control method of the refrigeration cycle apparatus 101 will be described. First, control during normal operation will be described.

  During normal operation, the degree of superheating of the working fluid at the suction portion of the compressor 102, which is the temperature difference between the suction temperature detection means 110d and the evaporation temperature detection means 110c, is calculated. Then, the expansion valve 104 is controlled so that the degree of superheat becomes a predetermined target degree of superheat (for example, 5K).

  Alternatively, it is also possible to further provide a discharge temperature detecting means (not shown) in the discharge portion of the compressor 102 and perform control using the detected value. In this case, the degree of superheat of the working fluid at the discharge portion of the compressor 102, which is the temperature difference between the discharge temperature detection means and the condensation temperature detection means 110a, is calculated. Then, the expansion valve 104 is controlled so that this superheat degree becomes a predetermined target superheat degree.

  Next, the control in the case of a unique operating state in which the possibility of the disproportionation reaction occurring will be described.

  In the present embodiment, when the temperature detection value of the condensation temperature detecting means 110a becomes excessive, the expansion valve 104 is opened, and control is performed to lower the high-pressure side working fluid pressure and temperature in the refrigeration cycle apparatus 101.

In general, in a refrigerant excluding carbon dioxide, it is necessary to prevent a supercritical condition from exceeding a critical point (a point described as _Tcri in FIG. 8 described later). In the supercritical state, the substance is neither a gas nor a liquid, and its behavior is unstable and active.

  Here, in the present embodiment, the temperature at the critical point (critical temperature) is taken as one guideline, and expansion is performed so that the condensation temperature does not approach within a predetermined value (5 K) from this temperature. The opening degree of the valve 104 is controlled. When a working fluid (mixed refrigerant) including R1123 is used, the temperature of the working fluid is controlled so as not to exceed (critical temperature−5) ° C. using the critical temperature of the mixed refrigerant.

Specifically, this will be described with reference to the Mollier diagram of FIG. In FIG. 8, a refrigeration cycle under an excessive pressure condition that causes a disproportionation reaction is indicated by a solid line (EP), and a refrigeration cycle under normal operation is indicated by a broken line (NP).

  If the temperature value at the condensation temperature detecting means 110a provided in the two-phase tube of the condenser 103 is within 5K with respect to the critical temperature stored in the control device in advance (EP in FIG. 8), expansion The valve 104 is controlled to open. As a result, the condensing pressure on the high-pressure side of the refrigeration cycle apparatus 101 decreases as shown by NP in FIG. 8, so that it becomes possible to suppress the disproportionation reaction caused by excessive increase in the refrigerant pressure. In the case where the leveling reaction occurs, it is possible to suppress the pressure increase.

  Note that the above-described control method for indirectly grasping the pressure in the condenser 103 from the condensation temperature measured by the condensation temperature detecting means 110a and controlling the opening degree of the expansion valve 104 is obtained when the working fluid including R1123 is azeotropic. Alternatively, if the temperature difference (temperature gradient) between the dew point and boiling point of the working fluid including R1123 in the condenser 103 is pseudo-azeotropy or is small, the condensation temperature is used as an index instead of the condensation pressure. This is particularly preferable.

<Modification 1 of Control Method>
Alternatively, as described above, by comparing the critical temperature and the condensation temperature, the high pressure (refrigerant pressure in the condenser) state of the refrigeration cycle apparatus 101 is indirectly detected, and an appropriate operation is performed by the expansion valve 104 or the like. Instead of the control method instructed to, the expansion valve 104 opening degree control may be performed based on the directly measured pressure.

  FIG. 9 is a Mollier diagram showing this control operation. In FIG. 9, the refrigeration cycle in which excessive pressure rise is occurring from the compressor discharge section to the condenser and the inlet of the expansion valve is indicated by a solid line (EP), and the above-described excessive pressure state is removed by a broken line (NP). The refrigeration cycle in the state is shown.

During operation, a pressure difference obtained by subtracting, for example, the condenser outlet pressure P _cond detected by the high pressure side pressure detecting means 115a from the pressure (critical pressure) P _cri stored in the control device in advance is determined in advance. (EP in FIG. 9), the disproportionation reaction has occurred in the working fluid containing R1123 from the discharge of the compressor 102 to the inlet of the expansion valve 104, Alternatively, it is determined that there is a high possibility that it will occur, and the opening degree of the expansion valve 104 is controlled to open so as to avoid sustaining the high pressure condition.

  As a result, the refrigeration cycle in FIG. 9 acts on the side where the high pressure (condensation pressure) decreases like NP in the figure, causing the disproportionation reaction to occur, or the pressure increase that occurs after the disproportionation reaction. Suppress.

  This control method is preferably used when the working fluid including R1123 is non-azeotropic, particularly when the temperature gradient is large at the condensation pressure.

<Modification 2 of control method>
Alternatively, instead of the control method based on the critical temperature or the critical pressure, a control method based on the degree of supercooling may be used. FIG. 10 is a Mollier diagram showing this control operation. In FIG. 10, a refrigeration cycle under an excessive pressure condition that causes a disproportionation reaction is indicated by EP, indicated by a solid line, a refrigeration cycle under normal operation is indicated by NP, and is indicated by a broken line.

Generally, in a refrigeration cycle device, the temperature of the refrigerant in the condenser is a certain level of the ambient medium by appropriate control of the refrigeration cycle such as expansion valves and compressors, heat exchanger size, and refrigerant charge optimization. Is installed to be higher. The degree of supercooling generally takes a value of about 5K. Similar measures are taken in working fluids including R1123 using similar refrigeration cycle equipment.

  In the refrigeration cycle apparatus in which the above measures are taken, if the refrigerant pressure becomes excessively high, the degree of supercooling at the inlet of the expansion valve 104 tends to increase as indicated by EP in FIG. Therefore, in the present embodiment, the opening degree of the expansion valve 104 is controlled on the basis of the degree of supercooling of the refrigerant at the inlet of the expansion valve 104.

  In this embodiment, the degree of supercooling of the refrigerant at the inlet of the expansion valve 104 during normal operation is assumed to be 5K, and the opening degree of the expansion valve 104 is controlled using 15K, which is three times the value as a guide. Yes. The reason why the supercooling degree as the threshold is tripled is that the supercooling degree may change within the range depending on the operating conditions.

  Specifically, first, the degree of supercooling is calculated from the detection values of the condensation temperature detection means 110a and the condenser outlet temperature detection means 110b. The degree of supercooling is a value obtained by subtracting the detection value of the condenser outlet temperature detection means 110b from the detection value of the condensation temperature detection means 110a. Then, when the degree of supercooling at the inlet of the expansion valve 104 reaches a predetermined value (15K), the expansion valve 104 is operated to open the opening, and the condensing pressure, which is the high-pressure portion of the refrigeration cycle apparatus 101, is decreased. (The broken line from the solid line in FIG. 10). Since the decrease in the condensation pressure is the same as the decrease in the condensation temperature, the condensation temperature decreases from Tcond1 to Tcond2, and the degree of supercooling at the inlet of the expansion valve 104 increases from Tcond1-Texin to Tcond2-Texin. And the degree of supercooling decreases (here, it is assumed that the working fluid temperature at the inlet of the expansion valve 104 does not change and is Texin). As described above, since the degree of supercooling decreases as the condensation pressure in the refrigeration cycle apparatus decreases, it can be seen that the condensation pressure in the refrigeration cycle apparatus can be controlled even when the degree of supercooling is used as a reference.

  FIG. 11 shows a pipe joint 117 that constitutes a part of the pipe of the refrigeration cycle of the present embodiment. When the refrigeration cycle apparatus 101 of the present invention is used for, for example, a home-use split type air conditioner (air conditioner), the refrigeration cycle apparatus 101 includes an outdoor unit having an outdoor heat exchanger and an indoor unit having an indoor heat exchanger. . Since the outdoor unit and the indoor unit cannot be integrated due to their configuration, they are connected at the installation location using a mechanical joint such as the union flare 111 shown in FIG.

  If the connection state of the mechanical joint is deteriorated due to a cause such as inadequate work, the refrigerant leaks from the joint part, which adversely affects the device performance. Moreover, since the working fluid itself containing R1123 is a greenhouse gas having a warming effect, there is a risk of adversely affecting the global environment. Therefore, it is required to quickly detect and repair the refrigerant leakage.

  The detection of refrigerant leakage includes a method of applying a detection agent to the site and detecting when a bubble is generated, a method of using a detection sensor, and the like, all of which require a lot of work.

  Therefore, in the present embodiment, a seal 112 containing a polymerization accelerator is wound around the outer periphery of the union flare 111 to facilitate refrigerant leak detection and reduce the amount of leakage.

  Specifically, the fact that polytetrafluoroethylene, which is one of the fluorinated carbon resins, is generated when a polymerization reaction occurs in the working fluid containing R1123 is utilized. The working fluid containing R1123 and the polymerization accelerator are intentionally brought into contact with each other at the leaked location, so that polytetrafluoroethylene precipitates and solidifies at the leaked location. As a result, it becomes easier to detect leaks visually, so the time taken to find and repair leaks can be reduced.

Furthermore, since the generation site of polytetrafluoroethylene is the leakage site of the working fluid containing R1123, the polymerization product is naturally generated and adhered to the site that prevents the leakage (Embodiment 4).
FIG. 12 shows a refrigeration cycle apparatus 130 according to the fourth embodiment of the present invention. The difference in configuration between the refrigeration cycle apparatus 130 shown in FIG. 12 and the refrigeration cycle apparatus 101 of the third embodiment is that a bypass pipe 113 having an opening / closing valve connected to the inlet and outlet of the expansion valve 104 is newly installed. In addition, a purge line having a relief valve 114 is provided between the outlet of the condenser 103 and the inlet of the expansion valve 104. The opening side of the relief valve 114 is disposed outside the room. In FIG. 12, the description of the temperature detecting means 110a to 110d, the pressure detecting means 115a, 115b, etc., described with reference to FIG. 7, is omitted.

  The control method described in the third embodiment (for example, the expansion valve so that the value obtained by subtracting the working fluid temperature measured by the two-phase pipe of the condenser 103 from the critical point temperature of the working fluid including R1123 is 5K or more. A control method for controlling the opening degree 104 and a control method for controlling the difference between the critical pressure of the working fluid and the pressure detected by the high-pressure-side pressure detection means 115a to be 0.4 MPa or more. Even when the 104 opening is opened, there is a possibility that there is no improvement in the pressure drop or a situation where the pressure drop speed is desired to be increased.

  Therefore, if the above situation occurs, the on-off valve provided in the bypass pipe 113 of the present embodiment is opened and the refrigerant is allowed to flow through the bypass pipe 113, so that the working fluid pressure on the high pressure side can be rapidly increased. The breakage of the refrigeration cycle apparatus 130 can be suppressed.

  Furthermore, in addition to the control for increasing the opening degree of the expansion valve 104 and the control of the on-off valve provided in the bypass pipe 113, if the compressor 102 is emergency stopped, the refrigeration cycle apparatus 130 can be further prevented from being damaged. preferable. In the case of emergency stop of the compressor 102, it is desirable not to stop the first transport unit 117a and the second transport unit 117b in order to rapidly reduce the working fluid pressure on the high pressure side.

  Even when the above measures are taken, if the disproportionation reaction is not suppressed, specifically, the difference between the critical temperature of the working fluid and the condensation temperature detected by the condensation temperature detection means 110a is less than 5K. Or, in the case where the difference between the critical pressure of the working fluid and the pressure detected by the high-pressure side pressure detecting means 115a is less than 0.4 MPa, the refrigerant pressure in the refrigeration cycle apparatus 130 further increases. Therefore, there is a need to escape the high-pressure refrigerant to the outside and prevent the refrigeration cycle apparatus 130 from being damaged. Therefore, the relief valve 114 that purges the working fluid including R1123 in the refrigeration cycle apparatus 130 to the external space is opened.

  The installation position of the relief valve 114 in the refrigeration cycle apparatus is preferably on the high-pressure side, and the condenser outlet shown in this embodiment is connected to the expansion valve inlet (at this position, the working fluid is in a high-pressure supercooled liquid state, so From the compressor discharge section to the condenser inlet (at this position, the working fluid exists in a gas state at high temperature and high pressure, It is particularly preferable to install it until the molecular motion becomes active and the disproportionation reaction itself is likely to occur.

  The relief valve 114 is provided on the outdoor unit side. In the case of this form, if it is an air conditioner, the working fluid is not discharged to the indoor living space, and if it is a refrigeration unit, the working fluid is not discharged to the product display side such as a showcase. As such, it is considered not to have a direct influence on humans, merchandise, etc.

  It is desirable for safety to open the relief valve 114 and stop the refrigeration cycle apparatus 130, for example, to turn off the power.

(Embodiment 5)
FIG. 13 shows a refrigeration cycle apparatus 140 according to a fifth embodiment of the present invention. The difference in configuration between the refrigeration cycle apparatus 140 shown in FIG. 13 and the refrigeration cycle apparatus 101 of the first embodiment is that the first medium temperature detection means 110e that detects the temperature of the first medium before flowing into the condenser 103. A second medium temperature detecting means 110f for detecting the temperature of the second medium before flowing into the evaporator 105, detection values of the temperature detecting means 110a to 110f, and the pressure detecting means 115a and 115b, The input power of the compressor 102 and the fluid machines 107a and 107b is recorded in an electronic recording device (not shown) for a certain period of time.

  FIG. 14 is a diagram showing the operation of the refrigeration cycle apparatus 140 of the present embodiment on a Mollier diagram. In FIG. 14, the refrigeration cycle indicated by EP indicates the condensation pressure when the disproportionation reaction occurs, and the refrigeration cycle indicated by NP indicates the refrigeration cycle during normal operation. In FIG. 14, the cycle change when the condensing pressure rises (for example, the difference in evaporation pressure between NP and EP, etc.) is not described for the sake of simplicity.

  The cause of the rapid increase in the condensation temperature of the working fluid including R1123 measured by the two-phase tube in the condenser 103 is (1) a rapid increase in the ambient medium temperatures Tmcon and Tmeva, and (2) the compressor 102 A pressurizing action due to a power increase, and (3) a change in the flow of the surrounding medium (an increase in power of one of the fluid machines 107a and 107b that drives the surrounding medium) can be considered. In addition to these factors, the action fluid-specific events including R1123 include (4) pressurization by disproportionation reaction. Therefore, in order to specify that the disproportionation reaction has occurred, it is a feature of the present embodiment that control is performed by determining that the events (1) to (3) have not occurred.

  Therefore, as a control method of the present embodiment, the expansion valve is opened when the amount of change in the condensation temperature of the working fluid including R1123 is large with respect to the amount of change in temperature or input power of (1) to (3). Control to the side.

  A specific control method will be described below. First, since it is difficult to compare the amount of change in temperature and the amount of change in input power value under the same standard, when measuring the amount of change in temperature, control is performed so that the input power does not change. That is, when measuring the amount of temperature change, the motor speed of the compressor 102 and the fluid machines 107a and 107b is kept constant.

  For example, the temperature change amount is measured at a certain time interval, for example, for 10 seconds to 1 minute. Prior to this measurement, for example, about 10 seconds to 1 minute before, the input electric energy of the compressor 102 and the fluid machines 107a and 7b is kept at a constant value. At this time, the amount of change per unit time of the input electric energy of the compressor 102 and the fluid machines 107a and 107b is substantially zero. Here, the zero is generally set to zero in the compressor 102, and in the fluid machines 107a and 107b, when the first and second media are ambient air, This is because the input power slightly fluctuates due to the influence of blowing or the like. That is, this substantially zero means that it is smaller than a predetermined value including some fluctuations.

  Under the above conditions, the change amount per unit time of the condensation temperature measured by the condensation temperature detection unit 110a is the change per unit time of the temperature of the first medium detected by the first medium temperature detection unit 110e. If the amount is larger than either the unit time of the temperature of the second medium detected by the second medium temperature detecting means 110f, it is considered that a disproportionation reaction has occurred, and the expansion valve 104 is opened in the opening direction. Control.

Note that the bypass pipe 113 is provided in parallel with the expansion valve 104 as shown in the fourth embodiment in preparation for the case where the pressure increase generated with the disproportionation reaction cannot be controlled only by controlling the opening degree of the expansion valve 104. A means such as an emergency stop of the compressor 102 or a relief valve 114 for reducing the pressure by discharging the refrigerant to the outside may be provided.

  Further, in the present embodiment, the control example of the expansion valve 104 performed based on the change amount of the temperature detection means installed in the two-phase pipe of the condenser 103 is shown, but the inlet of the expansion valve 104 from the discharge portion of the compressor 102 is shown. From this point, the amount of change in pressure at any point may be used as a reference, or the amount of change in the degree of supercooling at the inlet of the expansion valve 104 may be used as a reference.

  Note that it is preferable to use this embodiment in combination with any of Embodiments 3 and 4 of the present invention described above because further reliability can be improved.

  As described above, since the compressor and the refrigeration cycle apparatus according to the present invention are suitable for using a working fluid containing R1123, the compressor and the refrigeration cycle apparatus can be applied to uses such as a water heater, a car air conditioner, a refrigerator-freezer, and a dehumidifier.

DESCRIPTION OF SYMBOLS 1, 7 Airtight container 2, 8 Electric motor 3, 9 Compression mechanism part 10 Crankshaft 11 Orbiting scroll 12 Fixed scroll 13 Oldham ring 14 Frame 15 Compression chamber 16, 17 Bearing 18 Suction inlet 19 Outlet 21 Lubricating oil 22 Intake pipe 23 Discharge Pipe 30 Cylinder 31 Crankshaft 32 Piston 31a Eccentric part 34 End plate 34a Upper bearing 35 End plate 35a Lower bearing 36 Discharge valve 37 Cup muffler 38 Discharge port 39 Compression chamber 40 Suction port 41 Oil hole 42, 43, 44 Oil supply hole 46, 47 Space 45 Oil Groove 49 Suction Chamber 61 Compressor 62 Condenser 63 Throttle Mechanism 64 Evaporator 71 Power Feed Terminal 72 Glass Insulator 73 Metal Cover Holding Power Feed Terminal 74 Flag Type Terminal 75 Lead Wire 76 Donut-shaped Insulation Member 101, 130, 140 Refrigeration cycle equipment DESCRIPTION OF SYMBOLS 102 Compressor 103 Condenser 104 Expansion valve 105 Evaporator 106 Refrigerant piping 107a, 107b Fluid machine 108 Isotherm 109 Saturated liquid line, saturated vapor line 110a Condensation temperature detection means 110b Condenser outlet temperature detection means 110c Evaporation temperature detection means 110d Inhalation Temperature detection means 110e First medium temperature detection means 110f Second medium temperature detection means 111 Union flare 112 Seal containing polymerization accelerator 113 Bypass pipe 114 Relief valve 115a High pressure side pressure detection means 115b Low pressure side pressure detection means 116 Flow path 117 Piping joint EP State change of refrigeration cycle under excessive pressure conditions NP State change of refrigeration cycle during normal operation

Claims (15)

 A refrigerant containing 1,1,2-trifluoroethylene is used as a working fluid, polyol ester oil is used as a lubricating oil for a compressor, and it is fitted to at least one cylinder and an eccentric portion of a crankshaft provided in the cylinder. As a surface treatment of the crankshaft, the piston includes a combined piston, a vane that partitions the inside of the cylinder into a suction chamber and a compression chamber in accordance with the eccentric movement of the piston, and two end plates that close both end faces of the cylinder. The manganese phosphate film is applied, and the polyol ester oil includes a base oil, terpenes or terpenoids, and a lubricating oil having a viscosity higher than that of the base oil, and the high-viscosity lubricating oil includes the terpenes or The compressor characterized in that it is equal to or more than the terpenoids and the polyol ester oil has the same viscosity as the base oil. A refrigerant containing 1,1,2-trifluoroethylene is used as the working fluid, polyol ester oil is used as the lubricating oil for the compressor, and the fixed scroll and the orbiting scroll where the spiral wrap rises from the end plate are engaged in both directions. A compression chamber to be formed, and as a surface treatment of at least one of the fixed scroll and the orbiting scroll, a manganese phosphate film is applied, and the polyol ester oil includes a base oil, terpenes or terpenoids, A lubricating oil having a viscosity higher than that of the base oil, the lubricating oil having a viscosity higher than that of the terpenes or terpenoids, and the polyol ester oil having a viscosity equivalent to that of the base oil. Features compressor. The working fluid is a mixed working fluid containing difluoromethane, and the difluoromethane is 30 wt% to 60 wt%, or a mixed working fluid containing tetrafluoroethane, wherein the tetrafluoroethane is 30 wt% or more and 60 wt% or less, or a mixed working fluid containing difluoromethane and tetrafluoroethane, wherein the difluoromethane and tetrafluoroethane are mixed and the difluoromethane and tetrafluoroethane are combined. The compressor according to claim 1 or 2, wherein the mixing ratio is 30 wt% or more and 60 wt% or less. The compressor according to any one of claims 1 to 3, wherein the polyol ester oil comprises at least one selected from the group consisting of neopentyl glycol, trimethylolpropane, pentaerythritol, and dipentaerythritol as a constituent alcohol. .  The compressor according to any one of claims 1 to 3, wherein the polyol ester oil contains a phosphate ester antiwear agent.  The compressor according to any one of claims 1 to 3, wherein the polyol ester oil contains a phenol-based antioxidant. The compressor according to any one of claims 1 to 3, wherein an amount of the terpenes or terpenoids is 1% or more and less than 50% with respect to the amount of the 1,1,2-trifluoroethylene.  A motor unit for driving the piston or the orbiting scroll is provided, and the motor unit uses an electric wire formed by applying and baking a thermosetting insulating material on a conductor via an insulating film as a coil. Item 4. The compressor according to any one of Items 1 to 3.  The airtight container which contains the compression chamber and the motor part is provided, and the airtight container has a power supply terminal installed in the mouth part via an insulating member, and a connection terminal for connecting the power supply terminal to the lead wire. The compressor according to any one of claims 1 to 3, wherein a donut-shaped insulating member is disposed in close contact with the insulating member on a power supply terminal inside the sealed container.  The compressor according to any one of claims 1 to 9, a condenser that cools the refrigerant gas compressed by the compressor to a high pressure, and a throttle that depressurizes the high-pressure refrigerant liquefied by the condenser. A refrigeration cycle apparatus configured by connecting a mechanism and an evaporator for gasifying the refrigerant decompressed by the throttle mechanism by a pipe.  Condensation temperature detection means provided in the condenser is provided, and the opening of the throttle mechanism is adjusted so that the difference between the critical temperature of the working fluid and the condensation temperature detected by the condensation temperature detection means is 5K or more. The refrigeration cycle apparatus according to claim 10 to be controlled.  A high-pressure side pressure detection means provided between the discharge part of the compressor and the inlet of the throttle mechanism, the difference between the critical pressure of the working fluid and the pressure detected by the high-pressure side pressure detection means, The refrigeration cycle apparatus according to claim 10, wherein the opening degree of the throttle mechanism is controlled to be 0.4 MPa or more. Condenser outlet temperature detection means provided between the condenser and the throttling mechanism, and a condenser temperature detected by the condensation temperature detection means and a condenser outlet temperature detected by the condenser outlet temperature detection means The refrigeration cycle apparatus according to claim 11 , wherein the opening degree of the throttle mechanism is controlled so that the difference between them is 15 K or less. A first conveying means for conveying a first medium to be heat-exchanged by the condenser; a second conveying means for conveying a second medium to be heat-exchanged by the evaporator; and a condensing temperature detecting means provided in the condenser. First medium temperature detecting means for detecting the temperature of the first medium before flowing into the condenser; and second medium temperature detecting means for detecting the temperature of the second medium before flowing into the evaporator. A change amount per unit time of the input power of the compressor, a change amount per unit time of the input power of the first transport unit, and a change amount per unit time of the input power of the second transport unit in advance. The amount of change per unit time of the condensing temperature detected by the condensing temperature detecting means is smaller than the predetermined value determined per unit time of the first medium temperature detected by the first medium temperature detecting means. Change amount and second medium temperature detection hand In is greater than any variation per unit temperature time of the second medium to be detected, the refrigeration cycle apparatus according to claim 10 for controlling the throttle mechanism in the opening direction. The refrigeration cycle apparatus according to any one of claims 10 to 14, wherein an outer periphery of a joint of pipes constituting the refrigeration cycle is covered with a sealing agent containing a polymerization accelerator.